JPH06501092A - Anti-loosening screw element - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Anti-loosening screw element For threaded elements such as nuts, axial forces and possibly vibrations Various configurations are known for preventing loosening of tightened threaded connections under motion. It is. The simplest example is a lock with jagged sections on the axial surface. nut, the valley between the serrations is aligned with the horizontal hole of the screw, and the split bottle is inserted there. inserted horizontally. In this case, the need to provide a transverse hole in the screw is a drawback. In particular, prevention of loosening is only possible at a certain rotational position of the screw element, i.e. This is possible if exactly one of the valleys between the serrations coincides with the transverse hole of the screw. The situation is also a drawback. Another way to prevent screw connections from loosening is to install spring washers. Is Rukoto. One edge of the spring washer bites into the underside of the nut, and the other edge The edge bites into the opposing workpiece, and the spring washer adjusts to the nut depending on the direction of the edge. Prevent loosening. When tightened, the surface where the spring washer edges engage will be damaged. . The desired removal of the fixed screw connection is carried out against the action of the spring washer and Possible only under greater destruction of the gold engagement surface. In the end, the so-called lockna There is a threaded element in the shape of a ridge, and the contact surface of the threaded element has a radial direction in the shape of a notch on a file. The edge has a facing edge that digs into the facing surface, as in the case of a spring washer. There is. Of course, the drawbacks are similar to those of spring washers, and the formed knurling The eyes can be the starting point for fatigue failure (magazine ``Konsturkzione Φ Electronic J (1991) No. 4, February 20, 1991, 4 Page: EP-B1290967).

The problem of the present invention is that there is no need for the screw to have a special shape, and that contact is made during the fixing process. The object of the present invention is to produce a threaded element that can be prevented from loosening and whose surfaces are not damaged.

This object is achieved according to the invention by a threaded element according to claim 1.

The threaded element is usually tightened until the desired tightness is obtained in the threaded connection. Ru. The tightening ring is then twisted along the helical plane. By this, of course The bush-like extension, which is constructed with a correspondingly thin wall, is compressed in the radial direction, and the extension Since the internal thread of the screw is fixed to the screw, the tightening force is generated by the frictional force that prevents the screw from loosening. Attachment is achieved. To cause tightening, the connection between the body of the threaded element and the tightening ring must be Only relatively slight twisting of each other is required.

Actual fastened joints do not involve such processes. This is because, on the one hand, the screw threaded elements to obtain the desired axial force and to prevent loosening of the threaded elements. This is because the functions that operate them are completely separated. The contact surface is fixed by a fixed element. additional means to operate or activate the fixing means without damage due to without the need for an additional moment to be applied.

The screw element is tightened. Additionally, a bush-like extension with an internal thread is inserted in the radial direction. of the screw or the contact surface of the screw by compressing it to As the engagement increases, the local surface decreases when the axial force on the clamping connection is the same Surface pressure is reduced.

The use of helical surfaces to obtain radial tightening is described in British Patent No. 293122. It is more well known. The publication describes two overlapping rings, and the ring is The cylindrical inner surface of one ring fits onto the shaft, and the cylindrical inner surface of the other ring The outer circumferential surface contacts a corresponding hole in the outer member. two rings facing each other The circumferential surface is helical in a cross section perpendicular to the axis of the shaft. outer member When twisted toward the shaft, the two helical rings also twist their own spirals due to the friction ratio. are twisted around each other in the cylindrical planes, thereby realizing the tightening of the outer member on the shaft. Ru.

In its simplest embodiment, the threaded element consists of a body, a bush-like extension and a tightening link. Together with the locking nut, it forms the basic form of a locking nut, which according to claim 2 For example, the outer peripheral surface of the main body is formed with a shape for engagement with a rotating tool, for example. , has a circumferential longitudinal groove or radial hole for engaging a hook spanner, or It is usually hexagonally shaped.

According to claim 3, the clamping ring can also have a corresponding configuration.

The body of the threaded element and the tightening ring can thus simultaneously engage two rotating tools. , is effectively twisted with a high rotational moment to produce a tightening action on the screw. .

When twisting the body of the threaded element and the tightening ring together, the bush-like extension Too much of the applied rotational moment to compress the play in the screw In order not to waste money on overcoming, a longitudinal slit according to claim 4 is preferred. Preferably, the longitudinal slit significantly increases the circumferential stability and therefore the retention force of the fixation device. Significantly increases the deformation of the bush-like extension in the radial direction without significantly reducing the Make it bigger.

The figure shows one embodiment of the invention.

1 is a longitudinal section through the axis of the threaded element, and FIG. 2 is a longitudinal section along the line +1-1+ in FIG. FIG.

The threaded element generally designated 100 in Figures 1 and 2 is a locking nut; The lock nut is a screw or screw shown in dashed lines in FIG. 1 and having an axis 2. - Screwed onto spindle 1. The screw element 100 is in the form of a thick disk 4. It has a body 3, the thickness of which is approximately one third of the diameter in the illustrated embodiment. Disk 4 The outer circumferential surface 5 of is cylindrical and has four longitudinal grooves 6 equally spaced around the circumference, A hook spanner for rotating the screw element 100 can engage the longitudinal groove 6. can.

On the flat side of the disc 4, which is on the right in FIG. , the ridge 7 has an outer boundary surface 8 perpendicular to the axis 2; forms the contact surface of the threaded element 100. The contact surface of the screw element 100 tightens the screw 1. It comes into contact with an opposing surface formed on the member to be tensioned.

The disk 4 is provided with a female thread 9, which can be screwed into a corresponding male thread of the screw 1. Ru.

The screw 9 communicates with a bush-like extension 10 coaxial with the axis 2; 0 is provided on the flat side of the disc 4 spaced apart from the raised portion 7 . Therefore, screw 9 rests on the screw 1 over the entire length of the body 3 and the extension 10. The pitch of the screw is In relation to the thickness of the body 3, only a plurality of threads in the body 3 have a accommodating capacity. It has become

The axial bush-like extension 10 is arranged circumferentially along a plane passing through the axis 2. It has a vertical slit 11 that penetrates in the radial direction at a location, and the vertical slit 11 This allows the extension 10 to be easily compressed in the radial direction.

This radial compression is provided by a tightening ring 20, which It is rotatably installed on the outer circumferential surface of the axial extension, and there is no slit, allowing the extension It has a large cross section compared to the section. This is because the tightening ring 20 The axial extension 10 projects beyond the tightening ring 20 and away from the main body 3. On the outside, it has a circumferential groove 12 for accommodating a retaining ring 13 and is tensioned. The tightening ring, which is loose when not in use, is fixed to the extension part 10 by a retaining ring 13. Therefore, it is irremovably connected to the main body 3.

The outer circumferential surface 15 of the tightening ring 20 is also cylindrical in this embodiment, and there are sections provided around the circumference. It has longitudinal grooves 16 at some places. In order to twist the tightening ring 20 towards the body 3, use the lock. The spanner can engage the longitudinal groove 16.

The tightening device formed by the extension 10 and the tightening ring 20 is shown in detail on the basis of FIG. Describe. In the cross-sectional view, an assumed cylindrical surface 14 having a center point on the axis 2 is shown with a dashed-dotted line. It is shown in

The outer peripheral surface 17 of the bush-like extension 10 is defined by a helical surface 18 coaxial with the axis 2. The generatrix of the helical surface 18 is parallel to the axis 2. Tightening ring 20 The inner circumferential surface 27 of the It is formed as follows. The two helical surfaces 18.28 are the two first planes of the cross-section in FIG. In the quadrant of , it is located outside the assumed cylindrical surface 14, and the cylindrical surface is located at the "6 o'clock" position. 14 and is located inside the cylindrical surface 14 in the two later quadrants. Spiral The local radius of the shaped surface 18 is proportional to the angle clockwise from the maximum radius point 19 in FIG. For example, it decreases over approximately 360' and along the transition surface 22 at the point of minimum radius 21. Return to maximum radius again.

The inner peripheral surface 27 of the tightening ring 20 is configured accordingly. i.e. the radius moves clockwise from the maximum radius point 19' to the minimum radius point 21' in proportion to the angle. , and subsequently the inner circumferential surface 27 has a maximum radius at the transition surface 22' in a narrow angular range. Return to point 19'. The value of the pitch of the helical surface 18.28 in the circumferential direction is Once the lock is in the detent area and the tightening ring is tightened once, the rotation motor from the outside It is chosen so that it cannot be twisted back without ment. The diameter of screw 1 is 50m If the difference in radius is 2 degrees when m, the pitch will be approximately 2=150 during relaxation. An elongation condition (Keil) occurs, which is less than 1° and is The critical angle is approximately 7". In this example the helical surface 18.28 is extensive in the detent area. , which simultaneously reduces the rotational moment applied to the tightening ring 20 in FIG. The tightening device 10.20 is shown in a completely untensioned state. Perfect In the untensioned state, the transition surfaces 22, 22' are more circumferentially adjacent to each other. are doing. The tension function can be indicated by the threaded thread of the bush-like extension 10. By observing the point 19 of the helical surface 18 having the maximum radius. Figure 2 When the tightening ring 20 is firmly tightened, if the above-mentioned point is moved clockwise, the said point will be The helical surface 28 is contacted at points with increasingly narrower radii.

This forces point 19 radially inward. The same thing is true in verses 19 and 2. This applies to all other parts of the circumference except for the area that is free between the helmsman and the helmsman.

The axial extension 10 is thus uniformly radially compressed and threaded due to frictional forces. It will be tightened to 1. This ensures that the threaded element 100 can no longer be twisted and maintain the rotational position once achieved.

The difference in radius between points 19 and 21 is already As in the previous example, it is approximately 2 mm. Place the tightening ring 20 toward the bush-like extension 10. The radial tolerance of 0.2+sm was compensated for by twisting 36° at the time. You can This is sufficient in most cases. The considered tightening rotation stroke ( Anxugs-Drehhuebe) need never exceed 45°. Tightening When the ring 20 is twisted accordingly towards the axial extension 10, the transition surface 2 2' would be located at position 22', indicated by the dash-dotted line in FIG.

During operation, the lock is removed by twisting the body 3 until the interface surface 8 contacts the opposing surface. The threaded element forming the lock nut can be tightened. At that time, screw 1 The rotational moment that causes the tensile stress can be generated, for example, by a hook spanner engaging the groove 6. is applied to the main body 3 by. When tightening in this way, the screw element 100 is fixed In order to do so, it is never necessary to apply additional moments. i.e. circumference All rotational moments applied to 5 serve to tension the screw 1.

To obtain tension, tighten with a similar tool that engages the groove 16 of the tightening ring 20. Twist ring 20. This allows the bush-like extension 10 to be removed in the manner described. It is radially compressed and tensioned against the screw 1 by frictional forces. If necessary, other Even if the main body 3 is tightened with a rotary tool, the tension obtained with the screw 1 will not be maintained. Retention is achieved without change.

The fixation of the threaded element 100 is made within said element, forming a joint for the interface 8 There is also no engagement with the component or screw 1, and the fixation depends on the material of this facing surface. do not have.

The required length of the screw 9 is enlarged by the bush-like extension 10 and the axial length The radial compression in the area of the extension 10 also improves thread retention.

The main body 3 need not be just a nut, unlike the illustrated embodiment, but may also perform other functions. It may also be a supporting member. In the exemplary embodiment, only one extension 10 has a tightening ring 2 on one side. 0, but can be implemented on both sides and with two or more tightening ring supplements on the negative side. Submission of original translation (Article 184-8 of the Patent Law) September 6, 1993

Claims (1)

[Claims] 1. A screw element (100) capable of preventing loosening, comprising a disc-shaped body (3); a thread extending through the body (3) and having a accommodating capacity in the body (3); a female thread (9) having A bush-shaped extension ( 10) and The axis (2) of the internal thread (9) at the outer peripheral surface (17) of the bush-like extension (10) and is formed by a generatrix parallel to the axis (2) and has a detent a spiral surface (18) having a pitch in the circumferential direction; ), at least one rotatable and integral circumferential tightening ring; the tightening ring (20), and the inner circumferential surface (27) of the tightening ring (20) is Corresponding to and in contact with the spiral surface (18) of 10) Due to the helical surface (28), when the tightening ring (20) is rotated, Said extension (10) is radially compressed and said threaded element engages said internal thread (9). It has a tightening ring (20) that is tightened on the screwed male threaded part (1). threaded element. 2. The threaded element (100) is formed on the outer peripheral surface (5) of the main body (3). It is configured as a nut with features (6) for engagement by two rotating tools. Threaded element according to claim 1, characterized in that: 3. The tightening ring (20) has a feature (16) on its outer circumferential surface for engagement with a rotating tool. (15) The screw element according to claim 1 or 2, characterized in that it has the following characteristics. 4. Said body (3) is in the longitudinal region of said bush-like extension (10) said It is characterized by having a slit in the vertical direction along the plane passing through the axis (2). Threaded element according to any one of claims 1 to 3.